U.S. patent number 5,941,506 [Application Number 08/843,864] was granted by the patent office on 1999-08-24 for steam seal air removal system.
This patent grant is currently assigned to Electric Boat Corporation. Invention is credited to John H. Chapman, Kevin M. Didona, Glenn N. Levasseur, Daniel J. Link, James S. Smith.
United States Patent |
5,941,506 |
Smith , et al. |
August 24, 1999 |
Steam seal air removal system
Abstract
A turbine air sealing and condenser air removal system for use
in steam plant equipment is arranged to increase steam plant
efficiency, reduce oxygen concentration in condensate being
returned to the steam generators, and simplify system arrangement
and maintenance. This system incorporates dry running shaft seals
at the high and low pressure turbine shaft glands. The turbine
shaft glands are exhausted to a vacuum header which is exhausted by
vacuum pumps. Air from the condenser is also exhausted to the
common vacuum header. Non-rotating air seals on the turbine such as
valve stem seals, which must only accommodate linear movement, can
incorporate metallic bellows or conventional packings to prevent
air leakage into the steam path or steam leakage out into the
surrounding environment. The bellows seals may also incorporate
stem glands which are exhausted to the turbine exhaust trunk to
minimize the internal pressure of the bellows and prevent
catastrophic failure which might occur if the bellows were to be
pressurized with high pressure steam.
Inventors: |
Smith; James S. (Old Lyme,
CT), Levasseur; Glenn N. (Colchester, CT), Chapman; John
H. (Groton, CT), Link; Daniel J. (No. Stonington,
CT), Didona; Kevin M. (East Lyme, CT) |
Assignee: |
Electric Boat Corporation
(Groton, CT)
|
Family
ID: |
23939166 |
Appl.
No.: |
08/843,864 |
Filed: |
April 17, 1997 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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488299 |
Jun 7, 1995 |
5749227 |
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Current U.S.
Class: |
251/335.3;
137/312 |
Current CPC
Class: |
F28B
9/10 (20130101); F01D 11/00 (20130101); F01D
11/02 (20130101); F01D 11/04 (20130101); F01D
11/06 (20130101); Y10T 137/5762 (20150401) |
Current International
Class: |
F28B
9/10 (20060101); F28B 9/00 (20060101); F01D
11/04 (20060101); F01D 11/06 (20060101); F01D
11/00 (20060101); F01D 11/02 (20060101); F16K
031/00 () |
Field of
Search: |
;251/335.3 ;137/312 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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377-418 |
|
Jul 1990 |
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EP |
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2516-719 |
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Oct 1975 |
|
DE |
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1542483 |
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Mar 1979 |
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GB |
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Primary Examiner: Lopez; F. Daniel
Assistant Examiner: Woo; Richard
Attorney, Agent or Firm: Baker & Botts LLP
Parent Case Text
This is a divisional of application Ser. No. 08/488,299 filed on
Jun. 7, 1995, now U.S. Pat. No. 5,749,227.
Claims
We claim:
1. A metallic bellows valve stem seal comprising a valve stem, a
high pressure containment having at least one close clearance valve
bushing through which the valve stem passes, a metallic bellows
seal external to the high pressure containment through which the
valve stem passes into a low pressure zone surrounding the high
pressure containment and the outside surfaces of the metallic
bellows seal, the metallic bellows seal being substantially
attached to the valve stem and the containment so as to effectively
form a static fluid seal at each point of attachment, and a
leak-off connection for reducing the internal pressure of the
bellows below the pressure in the high pressure containment by
exhausting fluid leaking past the close clearance valve
bushings.
2. A metallic bellows seal as in claim 1 including a telescoping
guard surrounding the bellows.
Description
BACKGROUND OF THE INVENTION
This invention relates to a turbine sealing and air removal
arrangement which provides for conducting exhaust from both ends of
a turbine to a common vacuum header which also exhausts air from a
condenser. More particularly, this invention relates to a turbine
sealing and air removal arrangement for steam turbines which
reduces the oxygen concentration in the condensate being returned
to the steam generators, reduces maintenance, increases efficiency
and simplifies system arrangement. This invention also relates to a
turbine sealing and air removal arrangement incorporating a
metallic bellows valve stem seal which is exhausted to a turbine
exhaust trunk to minimize the internal pressure of the bellows and
prevent catastrophic failure.
Most conventional steam turbine air sealing/condenser air removal
systems are based on labyrinth type turbine rotor gland seals and
steam jet type air ejectors for exhausting air which leaks into the
turbine glands and the condenser. In the interest of minimizing
steam consumption by the steam jet air ejectors, two separate
exhaust systems are typically used for turbine rotor gland and
condenser air exhausting. Two separate systems are required due to
the fact that condenser pressure must be maintained as low as
possible, e.g., 0.5 to 10 inches Hg Absolute for best steam cycle
efficiency, while the outermost turbine rotor glands must be
maintained at slightly below atmospheric pressure in order to
prevent steam from leaking out of the turbine casing. The turbine
glands in such systems also require that sealing steam be provided
during start-up and at low power conditions to preclude air from
entering the condenser. This sealing steam requires still another
piping system to be installed and maintained. This system and the
steam supply to the steam jet air ejectors typically require that
reducing or pressure regulating valves be used, which unfortunately
are subject to steam erosion at the throttling element of the
valves. These regulating valves are commonly the source of
unplanned maintenance and plant downtime.
The steam sealing system also requires the use of a turbine rotor
turning gear that slowly rotates the rotor during start-ups from
cold iron and during temporary shutdowns to prevent bowing of the
turbine rotor due to differential thermal expansion. The rotor
turning gear is another high maintenance item that is also the
source of many operator errors for example, admitting steam while
the rotor is on turning gear. Operation of the rotor turning gear
is reputed to be the cause of over 90% of all turbine bearing wear
since the slow rotation of the rotor is insufficient to develop an
oil film which, at normal operating speeds, prevents the bearing
surfaces from contacting. For the reasons noted above, power
generating stations which employ steam turbines have historically
required constant attention by at least one skilled operator. This
is particularly undesirable in remote steam power applications
where small to medium units must be operated in relatively
unprotected environments such as petroleum distillation plants. The
recent proliferation of small to medium size cogeneration plants
has also demonstrated the need for steam equipment which can be
operated unattended for months or years with only occasional
planned maintenance being required and minimal capitol investment
at installation.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the invention to provide a turbine
air sealing and condenser air removal system for use in steam cycle
power generating equipment which is more efficient, less complex
and less expensive to install and maintain than systems currently
in use. The alternate system uses a common vacuum header for
condenser air removal and turbine rotor gland exhaust. The turbine
rotor glands incorporate dry running seals to prevent excessive
air/steam leakage into the vacuum header. Other steam/air seals
such as at the valve stems may include conventional packings or
metallic bellows, which provide an absolute, low maintenance
seal.
Another object of this invention is to provide a dry running
turbine shaft seal configuration which allows easy replacement of
seal elements when they become worn.
Another object of this invention is to provide a, metallic bellows
type valve stem seal which is a near absolute, long life seal and
is exhausted to vacuum such that failure of the bellows is
uneventful.
These and other objects of the invention are attained by providing
a power generation system including a vapor generation system
feeding at least one turbine, each turbine comprising a rotor and
sealing system including turbine rotor glands located along the
rotor, at least one condenser which condenses vapor from at least
one turbine and a common vacuum header. The common vacuum header
exhausts air from the turbine rotor glands thereby preventing the
air from mixing with vapor in the turbine and entering the
condenser. The common vacuum header is exhausted by an evacuation
device. This system minimizes the amount of dissolved gases in the
condensate returning to the vapor generation system.
The invention further provides a turbine rotor seal arrangement
including at least one row of stationary circumferential sealing
elements arranged for sliding contact with a cylindrical portion of
a turbine rotor. A spring arrangement holds the rotor seal in place
with respect to the turbine rotor. A split housing surrounds the
sealing elements and can be removed while the sealing elements
remain in contact with the turbine rotor. Such an arrangement
allows for easy repair and replacement of seal elements.
The invention also provides a metallic bellows valve stem seal
including a valve stem which extends from a high pressure
containment through one or more close clearance bushings and
through a metallic bellows seal into a low pressure zone
surrounding the high pressure containment. The metallic bellows
stem seal is substantially attached to the valve stem and the
containment so as to effectively form a static fluid seal at each
point of attachment. The internal pressure of the bellows is
reduced below the pressure in the high pressure containment by a
leak-off connection which exhausts fluid leaking past the one or
more close clearance valve bushings.
The invention further provides for a turbine rotor gland
arrangement having an outermost seal and an inner seal including
one or more labyrinth type seals. The gland formed between the
inner and outermost seal is exhausted so as to maintain pressure in
the gland at or below the pressure outside the outermost seal. The
outermost seal includes two rows of circumferential dry running
sealing elements. The outer row of sealing elements prevents air
leakage into the turbine while the inner row prevents leakage out
of the turbine in the event that the pressure in the gland becomes
greater than the pressure outside the outermost seal.
BRIEF DESCRIPTION OF THE DRAWINGS
Further objects and advantages of the present invention will be
more fully appreciated from a reading of the following detailed
description when considered with the accompanying drawings
wherein,
FIG. 1 is a schematic representation of a typical embodiment of a
power generation system arranged in accordance with the
invention;
FIG. 2 is a sectional view of a metallic bellows seal in accordance
with the invention;
FIG. 3 is a sectional view of a turbine rotor seal arrangement in
accordance with the invention for the high and low pressure end of
a turbine;
FIG. 4A is an enlarged sectional view showing the turbine rotor
seal arrangement at the high pressure end of the turbine depicted
in FIG. 3;
FIG. 4B is an exploded sectional view taken along line B--B of FIG.
4A;
FIG. 4C is an exploded sectional view taken along line C--C of FIG.
4A; and
FIG. 5 is a sectional view of a turbine rotor seal arrangement in
accordance with another typical embodiment of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
In accordance with the representative embodiment of the invention
schematically shown in FIG. 1 a vapor such as steam is supplied to
a turbine. In that embodiment, the basic system consists of a steam
generator 1 which provides steam to a turbine 5 via various
isolation valves 2, trip throttle valves 3 and governor valves 4.
Exhaust from the turbine 5 enters a main condenser 6 where the
exhaust vapor is condensed and returned to the steam generator 1 by
condensate pumps 7 and feed water pumps 15.
In steam plants such as shown in FIG. 1, an arrangement for
preventing steam leakage at valve stems and where the turbine rotor
exits the high pressure end of the turbine casing is an obvious
necessity. Additionally, an arrangement for preventing air leakage
into the low pressure turbine exhaust or the main condenser, which
will typically operate 20 to 29 inches Hg below atmospheric
pressure, must be incorporated. This is necessary because air, or
any non-condensable gas in the exhaust vapor will accumulate around
the condenser tubes as the moisture in the air/vapor mixture
condenses out, creating a boundary layer that impairs heat transfer
and overall condenser performance. Oxygen and other gases in the
air can also become dissolved in the condensate in high
concentrations if the amount of air in the condenser in excessive.
These gases, particularly oxygen, can cause corrosion problems in
the steam generator 1, and other portions of the system if they are
not removed on a continuous basis by use of feedwater chemical
additives or deaeration tanks. Air can enter the turbine exhaust
where the turbine rotor exits the low pressure casing under normal
operating conditions, and any other location where pressures below
atmospheric are encountered. Conventional steam sealing systems use
low pressure exhaust systems almost exclusively to eject air
entering the outermost gland at every mechanical penetration, e.g.,
valve stems, turbine rotors, etc., in the steam path. The air/vapor
mixture coming from these glands is ultimately routed to an
auxiliary condenser where the air is exposed to ideal conditions
for diffusion of gases into condensate forming on the condenser
tubes. Air which does not dissolve into the condensate will
accumulate near the high points of the auxiliary condenser which
are vented to atmosphere or must be ejected by some evacuation
method to prevent the condenser from becoming air-bound.
As shown in FIG. 1, in accordance with the invention air is removed
from the main condenser 6 by a vacuum pump 8 via an exhaust line 16
which is connected to a common vacuum header 17. The vacuum pump
discharges an air/vapor mixture drawn in from the vacuum header to
a moisture separator 9, where moisture in the air/vapor mixture is
separated and collected and relatively dry air is vented to the
atmosphere. The collected moisture is typically returned to the
condenser hotwell by a drain line. The drain line is opened by a
float valve when the level in the moisture separator tank gets too
high.
In an alternate embodiment a steam jet type air ejector may be used
to evacuate the vacuum header. In that case the vacuum header
discharges into an auxiliary condenser as described above to
separate moisture from the air/vapor mixture. Steam jet ejectors
are typically far less efficient than vacuum pumps and add a
considerable amount of heat and moisture to the air/vapor mixture
coming in from the vacuum header. This additional heat and moisture
necessitates the use of a sizable auxiliary condenser to remove
moisture from the air, rather than a simple moisture separator.
This sizeable auxiliary condenser has a large tube bundle surface
area, where condensate is formed in contact with high
concentrations of oxygen and other non-condensable gases, and thus
will return a larger quantity of condensate to the main condenser,
which promotes greater oxygenation of feed water. In contrast
vacuum pump moisture separators have a very small surface area
where precipitated moisture is exposed to oxygen and other
non-condensable gases. These separators need only remove moisture
coming in with the air/vapor mixture from the vacuum header since
the vacuum pump does not add vapor to the mixture as do steam
ejectors. The vacuum pumps, which are typically conventional liquid
ring type, require a small heat exchanger 10 to keep the liquid
ring-and moisture separator cool.
The steam plant air sealing and removal system shown in FIG. 1
includes two turbine rotor glands 11 and 12. These glands are
formed by incorporating a low leakage air seal where the turbine
rotor exits the turbine casing. The glands are connected to two
exhaust lines 13 and 14 just inside the low leakage air seals
forming the glands. The exhaust lines 13 and 14 are routed to the
common vacuum header 17. Conventional turbine steam/air sealing
systems use labyrinth type seals, which allow a considerable amount
of air leakage, dictating the use of a dedicated turbine gland
exhaust system. Simple carbon packing rings are sometimes used,
which do not require a dedicated turbine gland exhaust system, but
are limited to small turbine rotors. These simple carbon rings
allow a nominal amount of steam leakage out past the high pressure
gland and a nominal amount of air leakage in past the low pressure
gland, which enters directly into the condenser with turbine
exhaust.
These low leakage air seals, which are described in more detail
below, allow a nominal amount of air leakage into the turbine
glands. At high power levels, steam leakage from the first stage of
the turbine S into the high pressure gland 11 is common. It is
preferable to exhaust the air/steam mixture from the turbine glands
via the exhaust lines 13 and 14 to the common vacuum header 17 so
that air entering the turbine glands is exhausted to atmosphere
before it has a chance to enter the main condenser and become
dissolved in the condensate or impair heat transfer. However, if
the steam leakage from the first stage of the turbine 5 is too
excessive for a vacuum pump 8, moisture separator 9 and heat
exchanger 10 of a reasonable size, and the air leakage into the
turbine glands is within acceptable limits for the main condenser 6
to accept, the turbine gland exhaust lines 13 and 14 can be routed
directly to a turbine exhaust 53 via a separate exhaust line 54 or
via passages internal to the turbine casing structure. In either
case, the need for dedicated turbine gland sealing and exhaust
systems, as required in conventional steam plants, is
eliminated.
The valve stem seals for the system shown in FIG. 1 may be of a
conventional soft packing type with exhaust lines 18, 19 and 20
preferably running to the vacuum header 17. These exhaust lines may
also run to the turbine exhaust as shown for exhaust lines 18 and
19, since the air leakage through these paths will be negligible in
most cases. Soft packing type valve stem seals may also be
incorporated which do not use exhaust lines 18, 19 and 20. In that
case, however, steam will leak out from these seals as the packings
wear.
The present invention provides for an absolute air seal in the form
of a metallic bellows seal, which can also function to seal
internal steam pressure if desired. A metallic bellows seal may
also be connected to exhaust lines 18, 19 and 20 to reduce internal
pressure and hence, mechanical stress on the bellows, which
determines bellows fatigue life. However, no air leakage is
expected to occur. In this case, air contribution by exhaust lines
18 and 19 will be non-existent and a failure of a bellows will be
uneventful relative to a failure of a bellows seal under high
internal steam pressure, with the exception of a slight increase in
condenser air concentration or possibly generation of a whistling
tone.
FIG. 2 is a cross-section of a metallic bellows valve stem seal in
accordance with the invention which is compatible with the steam
plant air sealing and exhaust system described above. The valve
stem 21 is capable of linear motion only, i.e., no rotation is
possible, through bushings 22, which is the case for most root
valve, trip throttle valve and governing valve stems. A bellows
assembly 23 and upper and lower flanges 24 are attached to the
valve bonnet by threaded fasteners and to the valve stem 21 by a
nut 27. The upper flange seats on a tapered valve stem portion 28
to form a metal-to-metal seal, but may also incorporate a
compressible gasket or packing for improved tightness if an
acceptable surface finish on the seating surfaces of the upper
flange and the valve stem taper 28 cannot be maintained. The lower
flange is sealed against the valve bonnet using a compressible
gasket 26, which may also be implemented as a metal-to-metal seal
for simplicity, provided surface finishes are adequate on the
mating surfaces. Preferably, the metallic bellows 25 is a welded
type fabricated from formed convolutions of thin sheet metal. The
metallic bellows 25 may also be formed from a continuous tube or
electro-formed into the final shape required. The material for the
bellows convolutions must be suitable for high temperature, high
stress, high fatigue conditions such as NiCrFe, other nickel alloys
or the like. The bellows convolutions must be protected from
mechanical damage and from foreign objects which may become lodged
between the convolutions and cause high stresses when the bellows
is compressed. Therefore, a telescoping guard 29 is provided, which
consists of two or more concentric tubes connected to the upper and
lower flanges 24. The internal pressure of the bellows is reduced
to less than three atmospheres (absolute pressure), preferably to
atmospheric pressure or below, by connecting a leak-off connection
30 to the vacuum header 17 as shown on FIG. 1 or to the turbine
exhaust casing. Reducing the internal pressure, which would
ordinarily reach steam supply pressure, typically several hundred
PSI, without the leak-off 30, reduces stress on the bellows
convolutions which increases bellows fatigue life. Since the
bellows provide a near absolute air seal, the leak-off 30
represents no threat of increased air leakage unless a bellows
failure were to occur. Even in that case, the additional air
leakage should be minimal. Incorporation of the leak-off 30 ensures
that a bellows failure will be uneventful, since only a small
amount of air leaking into the bellows will occur. This leakage is
negligible compared to the large amount of steam leaking out of the
bellows which would occur if this leak-off were not incorporated in
the metallic bellows.
A cross-section of a typical turbine rotor air seal for
incorporation in the turbine air sealing/condenser air removal
system shown in FIG. 1 is shown in FIG. 3. The outermost gland
formed around the turbine rotor 31 is bounded by a dry running air
seal assembly 32 and labyrinth seals 33. The dry running seal has
sealing elements which include stationary carbon segments 34
arranged circumferentially around the turbine rotor 31. External
air pressure and garter springs 36 cause the carbon segments 34 to
be seated against the turbine rotor 31 while pressure venting
grooves 35 act to reduce the unit load on the circumferential
sealing surface. In this manner wear life of the carbon seal
elements is maximized. The carbon segments are seated axially
against a radial seal surface 37 by external pressure and
compression springs and spring plates 38. This seal configuration
provides a duplex seal capable of preventing air leakage from the
atmosphere on the left side of the seal to the gland on the right
side, during normal operation, or sealing against steam pressure
which may build-up in the gland on the right side of the seal under
a failure condition such as loss of cooling water to the condenser,
so that steam will not be released to the surroundings and endanger
personnel.
In an embodiment wherein the seal configuration shown in FIG. 3 is
implemented on the high pressure end of the turbine rotor the first
stage of the turbine is just to the right of the labyrinth seals
33. In that case the gland formed between the dry running seal
assembly 32 and the labyrinth seals 33 is exhausted to the vacuum
header 17 or to the turbine exhaust 53 shown on FIG. 1 via an
exhaust connection 39. The gland formed between the labyrinth seals
33 is exhausted to a downstream stage of the turbine, e.g., stage 4
or 5, via a packing re-entry passage 40 in order to make use of
high pressure steam leaking from the first stage area to the right
of the labyrinth seals 33. A flow restricting device, for example
an orifice, may be incorporated at the exhaust connection 39 to
raise gland pressure under high power operation. This will decrease
differential pressure across the dry running seal and as such, will
decrease unit loading on the seal faces, thus increasing the wear
life of the seal elements. Decreased differential pressure will
also minimize steam leakage from the packing re-entry gland or the
first stage area across the labyrinths which will improve steam
plant efficiency.
In an embodiment wherein the seal configuration shown in FIG. 3 is
implemented on the low pressure end of the turbine rotor, the
turbine exhaust is just to the right of the labyrinth 33. In that
case the exhaust connection 39 is connected to the vacuum header 17
shown on FIG. 1. Alternately, the exhaust connection 39 may be
omitted entirely if the air leakage past the dry running seal
assembly 32 is low enough for the condenser exhaust connection 16
shown on FIG. 1, to maintain condenser air concentrations within
acceptable limits. The labyrinth seals 33 may also be omitted.
However, retaining at least one labyrinth provides a back-up seal
which can prevent complete loss of condenser vacuum if the sealing
elements 34 in the dry running seal assembly 32 were to
catastrophically fail. The packing re-entry passage 40 does not
serve any purpose at the low pressure end of the turbine rotor, and
as such, may be omitted.
Although other types of dry running seals can be incorporated for
turbine rotor gland air sealing such as non-contacting face seals,
lip seals, various types of flexible circumferential seals, etc.,
the dry running seal configuration shown in FIG. 3 is preferable
for many reasons. As shown, the dry running seal assembly 32 fits
within the packing box constraints defined for the conventional
labyrinth seal assemblies that are used in conventional air removal
systems. In fact, if the grooves in the turbine rotor that would
normally be incorporated to accommodate the teeth of the outermost
labyrinth seal are machined away, a dry running seal configuration
as shown in FIG. 3 can be backfit into an existing turbine. This
seal can also accommodate almost unlimited axial movement of the
turbine rotor relative to the turbine casing which is sometimes
encountered due to differential thermal expansion of the rotor and
casing.
The dry running seal assembly 32 shown in FIG. 3 also permits
replacement of the carbon segments with minimal disassembly of the
packing box. By removing a packing box cap 41, access to the entire
seal assembly is provided. As shown in FIG. 4, once the packing box
cap 41 shown in FIG. 3 is removed, the upper half of a seal
assembly 42 can be removed, allowing access to the seal elements
34. Detaching the garter spring 36 allows each individual carbon
segment to be replaced. This can be accomplished without removing
the lower half of the seal assembly 43 by rolling the worn segments
out from around the turbine rotor and rolling the new segments in
underneath the turbine rotor.
Once the new segments 34 are installed and the garter spring 36 is
reattached, the upper seal housing 42 can be replaced. To prevent
interference of the spring plates 44 with the seal segments 34 when
the upper seal housing is lowered down onto the lower seal housing
43, shims 45 are placed in behind retaining rings 46 which capture
retaining pins 47 to the seal housings 42 and 43. The shims 45
spread the spring plates 44 so that a clearance will be present
when the upper seal housing 42 is lowered down onto the lower seal
housing. The shims 45 are removed once the upper half seal housing
is in place by pulling on a lanyard 48.
Each pin 47 is secured to a corresponding spring plate 44 by an
integral rivet 49 which is machined flush with the spring plate 44
as shown. The pin 47 passes through a spring 50 so that the spring
is physically captured and cannot be lost when the seal housings
are removed.
The lower seal housing 43 also incorporates drainage passages 51 to
permit any moisture which may collect at the low points of the seal
housing to be carried away. A soft packing 52 may also be
incorporated around the outside of the seal housing to minimize
leakage. This soft packing must be split in order to allow removal
of the upper housing 42.
An alternate embodiment of a turbine rotor seal arrangement for
implementation on the high pressure end of a turbine is shown in
FIG. 5. In this arrangement, the high pressure gland is provided
with a low leakage air seal 32 outside the gland and a low leakage
steam seal 55 on the inside of the gland. The low leakage air seal
32 is used to reduce air leakage into the vacuum header 17 or
turbine exhaust 53 of FIG. 1 as previously described. The low
leakage steam seal 55 is used to reduce steam leakage into the high
pressure gland from the first stage of the turbine 5 and
consequently into the vacuum header 17. This reduction in steam
flow reduces the heat load required to be condensed by the vacuum
pump heat exchanger 10. This reduction in steam flow also reduces
the total flow capacity that the vacuum pump 8 must be sized to
accept and improves steam plant efficiency by minimizing steam
leakage out of the turbine under high power operation. The method
of retention of the steam seal carbon segments, as well as
installation and replacement is similar to that described above for
the air seal assembly 32.
In summary, the present invention provides a simplified
arrangement, a method for preventing steam leakage out of,
minimizing air leakage into, and removing air from a conventional
steam plant which requires minimal operator attention, and
substantially reduced capitol investment and maintenance costs with
respect to conventional steam seal/air exhaust systems. The valve
stem bellows seal provides an absolute, long life air/steam seal
with easy access to the bellows, while the turbine rotor seal
provides an easily maintainable gland configuration with sealing
elements which have a very predictable, repeatable wear life.
Although the invention has been described herein with reference to
specific embodiments, many modifications and variations therein
will readily occur to those skilled in the art. For example, the
turbine rotor seals, power generation system, and metallic bellows
described herein are equally useful for turbines which utilize
fluids other than steam.
* * * * *